Hydraulic transmission



April 27, 1954 K. G. HLEN HYDMULIQ TRANSMISSION 7 Shets-Sheet l Filed July 22, 1948 Wi/q om* i Y m m FN: w mm Q w M m 8 om -q \I|m v Y M8* Qow WH wm* WN. W mm wm Qmv /L w: m? m; m 17 e 1 wow w i Nm. 1 Om IW 1 V V i-- w 3 www m vmom r mm Om w: om* www g v .wmv i Q a w w: I www om. mv mm N v v 0:. l. m 2 w w .MW 3 \r .bmw

April 27, 1954 K. G. AHLEN HYDRAULIC TRANsMIssIoN 7 Sheets-Sheet 2 Filed July 22, 1948 April -27, 1954 K. G. HLN 2,676,497

HYDRAULIC TRANSMISSION Filed July 22. 1948 7 Sheets-Sheet 3 m 92 m R v m m2 V V QS m m om* m2! m www 3? m L mm April 27, 1954 K. G. AHLN HYDRAULIC TRANSMISSION '7 Sheets-Sheet 4 Filed July 22. 1948 INVENTOR lATTORNEY April 27, 1954 K. G. AHLEN HYDRAULIC TRANsMIssIoN 7 shets-sneet 5 Filed July 22. 1948 i; nNvEN-rolg ArroRrEY 5 April 27, 1954 K. G. AHLEN HYDRAULIC TRANSMISSION 7 Sheets-Sheet 6A Filed July 22. 1948 mmm ' INVENTOR B g. Mfi

ATTORNEY Patented Apr. 273 1954 I f 2,676,491 HYDRAULIC rrmiNsr/ussIoN Karl Gustav hln, Stockholm, Sweden, assignor, by mesne assignments, to IIarvis C. Marble, New York, N. Y., Leslie M. Merrill, Westfield, N. J.,

'ATI-:NT lOFI-"ICE and Percy H. Batten, Racine, Wis., trustees Application July 22, 1948, Serial No. 40,076

The present invention relates to hydraulic power transmissions and has particular reference tosuch transmissions in which the hydraulic drive emhodies a Variable speed torque converter for producing an increase in the torque applied to the driven or output element as compared With torque delivered by the engine or other source of power to the input element of the transmission, and in which the torque converting hydraulic drive is employed in the transmission in conjunction with an alternative drive providing a relatively fixed speed ratio between the input and output members of the transmission and which is adapted to be used in alternation with the Variable speed torque converting hydraulic drive. More specifically the invention relates to transmissions of the above general character in Which the hydraulic torque converting drive is incorporated in the transmission with a positive mechanical drive to be used in alternation and 5 consideration in Which shifting of the drive from hydraulic to the alternative drive or vice versa may be efiected automatically in response to certain predetermined conditions of operation; in which such automatic shift is subject to an overruling control which will permit the shift from one type of drive to the other to be made at the will of the operator when the circumstances are such that such shift does not result in improper or ineflicient operation of the transmission under the existing circumstances; to provide improved means whereby such automatic and manual control may beV efected without deviation from the normal Operating habits of the operator of a vehicle in which the apparatus is installed; to provide improved means whereby'the required 8 Ciaims; Cl. 74-732) controls are simply and eifectively actuated by the reaction blading rotates counter to the direci tion of the pump and With the operation of the converter automatically shifted from single rotation to double rotation; and vice, versa, in accordance with predetermined Operating conditions; to provide an improved .organization in Which the above noted objects may be accomvplished in an' apparatus which is relatively simple mechanically and which may be incorporated in a design giving relatively very compact overall dimensions so that the appa-ratus may readily be installed in the comparatively limited space available in automobiles and like automotive vehicles; and to provide other and more detailed improvements in construction and Operating characteristics as will hereinafter more fully 'appear as the specification proceeds.

In order more fully to understand the nature of the invention, its several objects, and the manner in which they may best be obtained, there is set forth in the ensuing portion of this specification a description of different embodiments of apparatus for carrying the invention into effect, to which reference may be ha-d in conjunction with the a-ccompanying drawings forming a part hereof and in Which:

Fig. 1 is a longitudinal central section of a :transmission embodying the invention, certain portions of the mechanism in the upper right hand corner of the figure being rotated into the plane of the drawing for purposes of illustration;

Fig. 2 is a section taken on the line 2-2 of Fig. l;

Fig. 3 is a fragmentary section on an enlarged scale with certaintparts broken away looking from the right of vthe transmission as viewed in Fig. 2;

Fig. 4 is a section taken on the line 4-4 of Figs. l and 3;

Fig. 5 is a section taken on the line 5-5 of Figs. 2 'and 3;

Fig. 6 is a section taken on the line 6-6 of Fig. 3;

Fig. 7 is a section taken on the line 'I-'I of Fig. 2;

\ Fig. 8 is al schematic diagram illustrative of the fluid control systeml of thefparts shown in cated generally at ll] and adapted to be fixed to the bell housing or other fixedv part I2, of; for

example, an internal combustion engine, the crank or driving shaft of which is indicated at l4 and which for purposes of the present description may be considered as the power input or driving member. Rotatably mounted within the fixed housing Hi is the rotating converter casinglfi which in the present embodiment is driven through the medium of the engine flywheel 48 fixed to the shaft |4 and a drive element 20 rotationally fixed to the casing IG and driven from the fiywheel through the medium of the meshing teeth or splines 22.

The casing IB provides a chamber 24 for circulation of the hydraulic working fluid and also carries a ring of pump or impeller blades 26.

An axially central turbine member 28 is carried by a bearing 3G mounted on an intern-al extension Ita of the fixed housing and bearing 32 carried by the rotating casing IS, the latter being centered radially with respect to the engine shaft and flywheel by means of the annular flange 34 on the element 28 which engages a suitable bore in the fiywheel l8.

The turbine element is provided with a disclike portion 36 located in the hydraulic chamber 24 and carrying a row of turbine blades 38 which serve to support an internal ring member 40 which carries a second row of turbine blades 42. Between the rows of turbine blades 42 and 33 a row of reaction or guide blades 44 is supported by the disc-like portion 48 of a reaction member 48 which comprises in part a hollow shaft or sleeve portion 5D concentrically mounted around the sh-aft part of the turbine member 28 and supported by bearings 52 between the two shaft parts and hearing 54 between the reaction member and a radially inwardly projecting part of the rotating casing IB.

The shaft part 5D of the reaction member provides the inner race 56 of a freewheel clutch having engaging elements 58, which may be of blocklike form as shown in Fig. 2 or of the usual roller form acting against cam surfaces. The clutch engaging elements 58 are set so as to eng-age at times when under the influence of the hydraulic working fiuid the reaction member tends to turn counter to the direction of rotation of the pump or driving member.

The inner extension lila of the fixed housing lll, as seen more clearly in Fig. 2, is formed with i..

providing the outer race 64 of the overrunning clutch, which is engaged by the elements 58 and which is also provided with spaced externally projecting splines or teeth GS adapted to intermesh with the splines 60 on the stationary housing member. As will be evident from Fig. 2 the spacing of the splines 60 and 66 .in relation to their perpheral width is such as to permit the ring 62 to have limited peripheral movement, With the splines G0 and 66 acting as positive stops for determining the range of this movement.

For purposes to be hereinafter described there is provided an axially shiftable Operating pin or rod 68 mounted in the housing part Illa to move in a direction tangent to the circle of the ring 62 and adapted to be actuated by means *of -a suitable abutment 70 on ring 62.

For eifecting a direct mechanical connection between the driving member of the transmission and the turbine member a multiple disc friction clutch indicated generally at 12 is provided. This clutch comprises driving plates 74 rotationally fixed by and axially movable on suitable splines formed internally on the driving element 2!! and driven plates 76 rotationally fixed and axially movable on suitable splines formed on a disc part or Spider 18 keyed to and in effect forming a part of the turbine member 28. Clutch 12 is engaged by an Operating member SB in the form of an annular plate or piston located in a suitable recess of like configuration in the driving element 20, between Which and the plate 8G there are provided suitable packing rings 82 and 84.

In the present embodiment, the transmission is provided with a gear mechanism for transmitting drive positively in either forward or reverse direction from the turbine member and also providing la neutral position. This mechanism, which for convenience will be hereinafter referred to as the reversing gear, embodies a pressure fiuid actuated synchronizing clutch which advantageously is operated by the same hydraulic system as that Operating the direct drive clutch 12. In order to effect reverse1 the turbine member 28 is provided with a. gear 86 meshing with gear 88 carried by counter-shaft 90, which also carries gear 92. The tail shaft 94, which is carried by bearing 96 in the stationary housing and by a second bearing S8 between it and the turbine member 28, is provided with a hub portion lill] having external splines H32 on which is slidably mounted the annular reversing ring member |84 provided with teeth H18 adapted to engage a reversing idler gear 93 (Fig. 4) meshing with the counter-shaft gear 92.

A portion of the face of gear 86 on the turbine member is provided with teeth or splines NB adapted to engage With teeth 106 when the reversing ring member is shfted to a position to the left of that shown in Fig. 1, such shift being eifected by means of the reverse lever H0 turnable to rotate the reversing post H2 to which is fixed the shift yoke H4 having projections IMa engaging a suitable groove in the reversing ring m4. When the ring is shifted so that teeth H18 and IDB mesh, a direct forward driving connection is established between the turbine member and the tail shaft. In the position of ring l04 shown in Fig. 1 a neutral is established in which driving connection between the turbine member .and the tail shaft is broken. Movement of the reversing ring to the right of the position shown in the figure disconnects the direct driving connection and causes teeth IDG to mesh with the reversing idler gear so that reverse drive to the tail shaft is eifected.

Since normally, when in neutral position with the driving member turning, the turbine member 28 is also turning under the influence of the hy- -draulic drive, it is necessary in order to secure either direct or reverse drive without .clashing to synchronize the turbine member with the tail :shaft before the meshing teeth are brought into engagement, and for this purpose the pressure fluid actuated synchronizing clutch indicated generally at H6 is provided. The construction of this clutch is in general similar to that of clutch 12, comprising a number of what may be considered driving plates i IB splined on the tiwbine member and a number of driven plates |20 splined on the outer wall of a recess formed in the hub portion [00 of the tail shaft. A clutch Operating member l22 in the form of an annular plate is subjected to the action of pressure fluid in a manner here- ;inafterto be described; under the control ofzone 'or more control valves [24 which are actuated through the medium of a valve actuating ring [26 the position of which is controlled by means of the plates [28 (Fig. 4) fixed to turn with the post [2- and yoke [4. In Fig. 3 one of the plates [28 is more clearly shown and since plates [28 and the parts coacting therewith are duplicates, it will be suificient to describe but one. Plate [28 is provided with three notches [38, [32 and [34 between which there are cam surfaces [36 and [38. An Operating arm [48 provided with a projection [42 adapted to engage the notches in plate [28 is pivoted to the stationary casing on the pin [44 and is provided at its free end with proiecting lugs or ears [46 adapted to engage the valve actuating ring [26. The Operating arm [88 is held in engagement with the plate [28 by means of spring [48 (Fig. 1).

As will be seen from Figs. 1 and 3, when the reverse lever is in neutral position the projection [42 is engaged in the notch [38 of plate [28.l If the lever is moved to engage direct drive the first movement of the lever from neutral lifts the projection [42 out of thenotch [68 on to the cam surface [36, thus Swinging the arm [48 to the right as seen in Fig. 3 and to the left as seen in Fig. '1, or in other words forwardly with respect to the longitudinal axis of the transmission. This in turn moves the valve ring [26 and the valve or valves [24 in the same direction to admit pressure fluid to the synchronizing clutch Operating member [22. 'This serves to engage the clutch and, assuming the tail shaft to be stationary, acts to bring the turbine member to rest to permit the direct drive engaging teeth to be meshed without clashing. When direct drive position is reached the projection [42 drops into the direct drive notch [32 on plate [28 and under the action of the spring [48 the Operating arm [48 is returned to the neutral position in which pressure fiuid is cut off from the clutch so that the clutch is disengaged. When the reversing lever is moved from neutral position to reverse position, substantially the same action takes place, the projection on the operating lever L [48 being lifted out of the neutral notch and traveling along the cam surface [38 so that the control valve or valves admit pressure fluid to engage the synchronizing clutch until after the reverse gear teeth have been meshed, when the projection [42 drops into the reverse notch [34 to cut off pressure fluid and permit the clutch to disengage. i

As previously noted, both clutches '[2 and [[6 are advantageously controlled by a common hydraulic pressure system which will now be described with reference particularly to Figs. *1, 2, 3 and 8. The stationary housing [8 provides a sump [58 for liquid for Operating the hydraulic torque lconverter and also for the operation of the clutche's. A pump [52,'preferably of the gear type, is carriedby the extension [8a of the stationary housing, this pump being driven by means of'gar [54 carried by the rotating casing [6 and meshing With the gear [56 on the pump shaft. Pump [52 draws liquid from the sump through the inlet connection [58, preferably provided with a suitable strainer [68, and delivers fluid under pressure through a discharge conduit [62 to a master control valve indcated generally at [64. This control valve comprises a housing [66 having a cylindrical bore in Which is slidably mounted the valve member [68 for controlling flow of pressure fiuid diseharged from the pump to the conduits [18 and [72, and return flow through condut'l'l '[4 and [16,l as appears more clearly from the flow diagram of Fig. 8. In the structural embodiment, the pressure conduits ['[8 and ['[2 are, as shown in Figs. 1 and 2, formed by suitable bores in the stationary housing extension [8a. The pressure conduit [62 is formed by a bore in the pump housing [66 while the return conduit ['[6 is formed by a further bore in the housing lying outside the plane of Fig. 2 (see Fig. 3). The conduit ['[4 is provided by a further bore (Fig. 2) which joins the bore ['[6 as indicated in the diagram of Fig. 8. Bore ['[6 is in communication With a spring loaded pressure relief valve ['[8 while the pressure conduit [62 from the pump is in communication with a second pressure relief valve [88. The spring loads on these two valves are adjusted so that valve [18 will be opened by a lower value of fiuid pressure than valve [88 and for the purposes of this description these valves may therefore -be referred to respectively as low pressure and high pressure relief valves. As will be seen more clearly from Fig. 1, the pressure conduit ['[2 communicates with a pressure chamber [82 located between the stationary housing portion [Ga and the rotatably mounted turbine and reaction members.

The forward end of this chamber is blocked off by a suitable diaphragm member [813 having suitable pressure packed relation with respect to the portion of the rotating casing carrying the pump gear [64 and the shaft portion of the reaction member. The shaft part of the turbine member 28 is provided with one or more longitudinally extending grooves or channels [86 which are placed in communication with the pressure chamber [82 by i means of one or more radial holes [88. The hydraulic working chamber 24 is placed in communication with the channels [86 by means of one or more radial openings [98 in the turbine shaft at the forward end of channels [86 and ports [82 passing through the disc portion 36 of the turbine member. Ports [94 in the clutch spider '[8 admit pressure fluid to the space [86 between the driven element of the clutch and the driving element 28, there being a piston ring seal [88 between these parts to separate the space [86 from the chamber or space 288 between the driving element 28 and the forward end of the turbine member 28. Space 288 is placed in communication with the recess in which the clutch Operating plate moves by means of one or more radially extending bores 282 in the element 28.

An axially central bore 284 in the turbine member 28 communicates at one end with the space or chamber 288, and at its other end communicates with one or more radial bores 286 which extend to the surface of the shaft of member 28 at places peripherally spaced between the axially extending channels [86 in member 28. Bores 286 communicate with an annular external groove 288 on the turbine member which in turn communicates with the conduit [18 leading from the control valve.

The channels [86 of the turbine member extendk rearwardly to communicate with radial bores 2[8 which conduct pressure fluid to the valve chambers in which the control valves [24 are located, these valve chamber-s being vented by means of passages 2l2.

The operation of this system under the control of the master valve [64 is as follows, it being assumed that hydraulic working fiuidV under pressure is being supplied by pump [52 through the conduit [62, the maximum pressure of the fluid being determined by the high pressure relief valve [88. In the position of the control valve shown in Fig. 8 the apparatus is set for hydraulic drive, since the pressure supply conduit |2 is connected by means of conduit H2.

vchamber 182, channels |86 and ports 195 and H32 with the working chamber 24 of the converter so that the Working fluid is maintained in this chamber under a predetermined minimum static pressure, the value of which is governed by the loading of the relief valve 180. The hydraulic fluid under pressure also, through hearing 32 and ports [94, is adrnitted to the chamber [96 and from this chamber has access to the chamber in which the clutch plates of clutch 72 are located and to one face of the clutch Operating member 8G. The hydraulic fluid thus operates to separate the clutch plates and also acts on the Operating member 80 to retract the latter so that the clutch is disengaged. This is a certain amount of leakage of the pressure fiuid past the piston ring seal IBS, -the leakage fiuid flowing to chamber NEJ-'and from there through the bores 284 and 296, groove 28 and conduit HG to the master valve which in this position of the valve connects conduits I'I and H6, to permit ficw of leakage fiuid back to the sump. The desired pressure differential conduit ll and through the groove 298 and bores 206 and 294, chamber 200 and bores 252 the fiuid is admitted behind the clutch operating plate Bi) so that the clutch is engaged and a direct mechanical drive connection established between the power input member and the turbine member for the establishment of direct mechanical drive. A certain amount of pressure fluid leaks from chamber 200 past the piston ring seal i98 to chamber |96, and through ports I84, bearing 32, ports |92 and lim, chan- -nels 185 and chamber |82 is returned to the conduit I'I2, Which in the assumed position of the valve member IBS is in communication with the conduit H4 which returns the leakage fluid to the sump, while desired minimum pressure of the leakage fiuid is maintained by valve H8. This in turn serves to maintain a desired minimum static pressure in the working chamber 24 of the converter, in which it is desirable to maintain a certain value of static pressure even though the hydraulic mechanism is not in action.

When the master valve is set in the position shown in Fig. 8, which provides for converter drive, the Channels ISG, as previously explained, are lled with high pressure actuating fiuid so that this high pressure fluid is available for en- -gaging clutch H6 to provide synchronization for either direct or reverse drive. The manner of actuating the control valves [24 by manipula- .nections 2! 2. In this .connection it is to be noted that whether in forward or reverse drive the clutch rotates and centrifugal force will ordinarily be sufiicient to cause the clutch Operating fluid to be thrown out of the Operating chamber, creating suffieient vacuum to cause disengagement of the clutch plates so that the clutch does not remain engaged when the gear is shifted from a driving position back to its neutral position. Obviously, dished plates or other means such as retracting springs may be employed to insure disengagement of the clutch when engaging fiuid is not admitted to it.

It is desirable that reverse drive be obtained only when the transmission is set for hydraulic drive and not for direct mechanical drive. Means to be described later have therefore been provided which insures that the master control valve is always set to the position giving hydraulic drive before the synchronizing clutch can be engaged.

It is characteristie of hydraulic torque converters of the kind under consideration that as the speed of the turbine or driven member approaches that of the pump or driving member the ratio of the secondary torque to the primary torque, Which is ordinarily maximum when the turbine member is stalled, decreases until a point is reached where the input and output torques are equal and if the speed of the turbine member relative to the speed of the pump increases beyond this ratio the output torque becomes less than the input torque. Obviously no advantage and considerable disadvantage is involved if the speed of the turbine member relative to that of the pump member is permitted to rise above the value at which no torque increase is obtained and at or before the speed ratio where no torque increase is produced it is desirable to shift from the hydraulic drive to an alternative form of drive which in the present instance is a direct mechanical drive. The ratio at which this change should be made is usually referred to as the shift point of the transmission.

In accordance with one of the aspects, of the present invention an automatic control for effecting shift from hydraulie to mechanical drive is provided, and the mechanism by means of which this is efiected will now be described.

Referring more particularly to Figs. 2 and 3, a bell crank type of lever 2I4 is pivoted on a stud 2 it carried by the extension i Da of the fixed housing. Lever 2l4 has an arm 258 located to be contacted and moved by the actuating rod 68 associated With the overrunning clutch which holds the reaction member against counter-rotation. The second arm 220 of lever 214 is provided With a laterally extending lug or ear 220a sei-Ving as an abutment for a spring 222 which is held in compression between'v the lever and in a suitable seat on the housing part Milia. The force exerted by Vthe spring and tending to move .the lever 2l4 in counter-clockwise direction as viewed in Fig. 2 may be varied by turning the stud 224, which is threaded in the ear 22912 and Which carries the spring retaining cup 226, so as to shorten the length of the spring in any given position of the lever 2l4.

An extension 22522; on arm 220 is provided with a slot engaging the head 228 of the master control valve member I Gli so that the latter is actuated by movement of the lever.

In addition to providing for automatic shift from--hydraulic toy mechanical drive, it is also desirabletoenable the operator to overrule the automatic shift so as to be able to effect shift from one type of drive to the other at will, and as has previously been mentioned it is desirable to provide means for preventing engagement of reverse unless the master control valve is set to provide hydraulic drive. To secure this latter function an interlocking mechanism is provided which comprises a lever 230 Which is pivotally mounted intermediate its ends on a pin 232 carried'by suitable ears' on the stationary housing 10. One arm 230a (Fig. 6) is provided with an abutment surface 230b adapted to engage the extension 220b of lever 2I4. The other arm 230c of lever 230 is provided with a projection 230d. The shift yoke II4 is provided at one side with a depending extension Il4b which at its lower end is provided with a transversely extending arcuate arm IItc provided with a cam face comprising' two porticns II4d and Ilte parallel with each other but oifset and joined by the camrise II4f.

With Vthe reversing lever IIO set as shown in Fig. 1 so that the parts are in neutral position, the position of the extension H43) of the yoke H4 is as shown in Fig. 6 so that the projection 23011 of lever 230 is in engagement with the cam surface I I4e, which holds lever 230 against clock-- wise turning movement as viewed in Fig. 6 and maintains the abutment surface 23th substantially in contact With the extension 2201) on the lever 2I4. With the parts in these positions it will be seen from Fig. 2 that the lever 2 I4 is prevented from turning counter-olockwise from the position shown in Fig. 2 and with the lever in the position shown the master valve I64 is set to the position -which corresponds to that shown in Fig. 8, which as previously described provides hydraulic drive.

If now the lever I I is shifted to engage reverse, the extension II4c of the shift yoke H4 moves to the left as seen in Fig. 6 so that the projection 230d moves along the cam surface I44e, which operates to continue to hold the lever 2I4 and the master valve I04 in the same position, thus insuring that the mechanism is set for hydraulic drive if reverse is engaged.

On the other hand, if forward drive is desired the shift yoke is turned in the opposite direction 'so that the extension I I4c moves to the right as seen in Fig. 6 and the projection 232 p'asses down the cam rise H41* to the cam face II 4d. This permits lever 230 to turn clockwise as seen in Fig. 6, the lever 2I4 then being, so far as lever 230 is concerned, free to move counterclockwise as seen in Fig. 2 under the influence of 'the spring 222. Counter-clockwise movement of lever 2I4 from the position shown in Fig. 2 will operate 'to shift the master valve to a position providing for direct mechanical drive, so that when the shift yoke is set for forward drive the master valve can be in either of its two positions, depending upon the position of lever 2I4, the position of the latter, however, being determined under different conditions by other factors hereinafter discussed.

Insofaras the automatic shift from hydraulic to direct drive is concerned, the manner in which the position vof lever 2I4 is shifted to effect this function will later be described, but as previously noted it is desirable to provide a manually controllable overrule mechanism by means of Which hydraulic or direct drive can be secured at will, subject to certain limits operative to prevent the operator from overruling the automatic shift to establish direct drive under conditions when such drive should not be employed.

The overrule mechanism comprises an operating lever 234 (Fig. 2) operative to turn an overrule control member indicated generally at 2%, rotatably mounted in a suitable bearing carried by the stationary housing ill. Member 235 is provided With an arcuate arm portion 23611 provided with notches 238, 240 and 2ii2 (Fig. 7) adapted to be engaged by a position retaining pin 244 resiliently loaded by the spring 2138 carried in a suitable bore in the housing iii. An arm 2361) -is provided which depends from the rotatably mounted post portion of member 236. This arm at its lower end comprises a section 2330 lying in a plane normal to the axis of turning movement of the member 235, a section 236d extending obliquely to one sidel of said plane and a section 2366 extending obliquely to the other side of said plane.

The arm 220 of lever 2I4 is provided with a laterally projecting extension 2200 in which there is located a slot 248 through which the arm 23th of member 236 extends. As will be seen more clearly from Fig. 5, the width of the slot 248 is substantially greater than the thickness of the arm '23612 to permit lateral movement or play between the parts. Also the arm 2200 is provided with a bore for the reception of a spring 250 acting on a pin 252 tending to resiliently hold the arm 2361) in spaced relation with respect to the wall 24'8a. of the slot 248.

In the position of the parts as shown in the figures the overrule lever is in its neutral position which will permit freedom of movement of the lever 2I4 under the influence of the automatic control, provided that the reversing mechanism is not set for reverse drive, which provides the interlock preventing lever 2I4 from assuming a position under such conditions which will permit of a direct drive connection through the transmission.

If the lever 234 is shifted so as to bring the lever upwardly from the plane of the paper as seen in Fig. 2, the member 236 is turned clockwise as viewed in Fig. 7 to bring the retaining pin 244 into the notch 242, and the arm 23th is moved downwardly as viewedI in Fig. 5 to bring the section 23d into contact with the wall 2481) of the notch 248 in lever 2I4. This provides a positive mechanical lock preventing movement of lever 2I4 in counterclockwise direction from the position seen in Fig. 2 and consequently insures positioning of the master valve I64 so that the mechanism is set for hydraulic drive.

If, on the other hand, the lever 234 is turned downwardly behind the plane of Fig. 2 the reverse action takes place, the pin 244 being shifted into the notch 240 and the arm 23th being moved up- Wardly as seen in Fig. 5 to bring the oblique section 236e into contact with the pin 252 so as to resiliently move the lever 2 I 4 in counter-clockwise direction and shift the valve I64 to the position effecting direct drive.

As previously described, the interlocking lever 230 prevents movement of lever 2I4 in counterclockwise direction from the position shown in Fig. 2, to effect direct drive positioning of valve I64, if the mechanism is set for reverse drive. Consequently, the manual overrule mechanism must be provided with a safety interlock Which will prevent the overrule from shifting the mechanism to direct drive position if the reversing mechanism is engaged in reverse position. Thls safety interlock is provided by the spring 250 and the resiliently loaded pin 252.

m If for example it is assumed that the reverse gear mechanism is in either neutral position or If under the assumed condition, it were attempted by means of the overrule mechanism operated by lever 234 to shift to direct drive this would not be possible since the resulta'nt movement of the arm 23612 upwardly as seen in Fig. to'

bring the section 236e in contact with pin 252 would merely result in retracting pin 252 against the pressure of spring 2511'I without resulting movement of lever 2l4. If this resilient connection, which in 'effect under certain conditions constitutes a lost motion connection, were not employed, damage 'or breakage of the parts might be 'caused by the cam action of the section 236e attempting to shift a member in a direction prevented by the abutment formed by the proj'ec; tion 230b on lever 230. V V

The operation of the above described apparatus is as follows. In the position 'of the parts shown in the figures and assuming the apparatus to be driven by a lconventional righthand engine,

the direction of rotation vof the pump and turbine elements will be counter-'clo'ckwise in Fig. l2 as indicated by the arrow 254. Since the reverse gear parts are in neutral position the lever 2l4' is held in the position of rotation shown in Fig.

2 by the action of spring 222 and that of the abutment 2302) which limits the counter-clockwise movement of the lever under the influence of the spring.

Since no torque is transmitted 'under the assumed conditions, the reaction member of the converter will 'also tend to rotate in counterclockwise direction as seen in Fig. 2, this movement being permitted by the action *of the overrunning clutch. Due vto the unavoidable friction i in the clutch even when 'overrunm'ng, the outer clutch ring 62 will be moved counter-'clockwise to one of its limit positions deterrnined -by the engagement of the 'splines 60 and 68. In this position of the parts 'there is a certain amount to move from the cam surface ll-4e to the cam surface lldd. This permits the vabutment 23th to move to the right as seen in Fig. 2 Iand further permits counter-lclockwise movement of lever 2I4 from the position seen in Fig. 2 under the influence of spring 222 so a's to take up the play between the lever arm 2l8 and the abutment 10, between which parts the Operating rod 68 is 'held in compression. For the purposes of describing the present action lit is further-assumed that'the overrule lever 234 'is in neutral position so as to have no influence on the automatic action, lever 2|4 being able yto move counter-clockwise Ifrom vthe position shown in Fig. 2 Aiinsofar as the overrule mechanism isconcernedidue to the'clearanc'e in the slot 248.

If it is assumed th'a'tthe vehicle is standing still with the reversing gear in neutral position and with engine idling, a -shi'ft to enga'ge 'forward drive will operate first to stop rotation of the turbine member of the converter. With v i -12 'this member sta-tionary, reaction tordue will be applied to the reaction member by the working fiuid being circulated in the converter and this torque will operate, through members 62 and 68 to maintain lever 2I'4 in the position shown in Fig. 2, against the action of spring 222, even though the lever Elli is free to turn counterclockwise from the position shown so far as any stop provided by abutment 23012 is *'concerned. Thus, under starting conditions for forward drive, valve l is held in the position determining hydraulic drive by the action of reaction torque instead of by a positive mechanical lock of the kind which is effected when the mechr anism is set for reverse drive.

As long as sufficient power is being trans'- mitted through the hydraulic Circuit and further as long as the ratio between the speeds 'of the driving and driven members of the hydraulic mechanism is such that appreciable torque multiplicatio'n is being effected, the hydraulically applied reaction force on the reaction member, acting through the overrunning clutch and the movable ring 62, will maintain the latter in its terminal position which holds the lever 2 l4 and valve 164 in positions maintaining hydraulie drive. However, if and when the speed 'of the turbine member relative to the pump 'or -'driving member rises to a ratio "such that "no torque increase is accomplished by the hydraulic mechanism, at which time no reaction torque would be applied to the reaction blades ending to turn them counter to the direction of the pump vand tur-bine, spring 222 acts to turn lever 2 ['4 counterclockwise and shift the control valve H54 to its position electing shift to direct drive. If it lis desired to have the shift from hydraulic to direct drive automatically made exactly at, the theoretical shift point'where the torque ratio between input and output is exactly one to one, then the tension of spring 222 should be set 'so that it exerts only enough force, to overcome the frictonal resistance of moving the valve 164 and shifting the ring 62 from one to the other of its terminal positions. In some instances it m'ay be desirable to have the automatic shift to direct drive 'effected while there is still some vincrease in torque efiected by the hydraulic drive. This may readily be veffected by increasing the tension of spring 222 so that it is sufficient not only to overcome the friction necessary to effect the shift but also to shift the ring 62 in counterclockwise direction as seen in Fig. 2 before lthe value of the hydraulically applied reaction 'force acting on the reaction blades and 'tendin'g to turn the ring 62 in clockwise direction as 'seen in Fig. 2 drops to zero.

With the apparatus set for forward 'drive s'o that either hydraulic or direct drive is available in accordance with Operating conditions, it may be desirable to shift from hydraulic drive to direct drive 'when the speed of the turbine member reiative to that of the pump member is lower than that required to effect the automatic shift. This is accomplished by the overrule mechanism vthe operation of which will be generally un-derstood from the previous ldefscription. If direct drive is desired at a time when the automatic control leaves the mecham'sm in hydraulic drive the overrule lever is depressed as seen in Fig. 2 to bring the section 2366 of the arm 23617 into vcontact with the "pin 252 and turnthe lever 2|4 counter-clockwise 'so as to move the control 'valve H58 to the right as seen in Fig. 'Zand shift to direct drive. This ifs" overrule ability should not, however, be available under conditions where high values of torque are required to be transmitted through direct drive position the section 2356 acting on.

pin 252 has to move the lever fit counterclockwise not only against the resistance of the control valve which must be shifted but must also turn lever 2!!! against the existing reaction resistance applied to the. ring -2 and the Operating rod 63. Consequently, dependingupon.

the strength of the spring Z in relation to the reaction resistance exerted vthrough the operating rod 6.8, the manual overrule for shift-l ing to direct drive may be effective or inefiective. If the degree of torque multiplicaticn and the resulting hydraulically applied reaction is too high to warrant shifting to direct drive, then theforce required to shift lever Ett will be more than can be effect-ed through the spring 259 and instead of the overrule member moving lever 2il itwillmerely operate to retract the pin 252. On

the other hand, if a shift to direct drive is warranted. the hydraulic reaction, resisting movement of the lever 2iil, will be insuficient to compress spring 25%, so that movement of the overrule member will move the lever and the i control valve to the direct drive position.

For return from direct to hydraulic drive the overrule mechanism is employed, the overrule lever being turned so as to be lifted out of the plane of Fig. 2, causing the section 2% of 'the arm 23th to engage lever 234 and shift the control valve lr-"i to the hydraulic position. Depending upon the nature of the control desired. many different arrangements may be employeol for affecting this under the control of the opera-tor, as for example by suitablelinterconnectionwith the vengine throttle or with the brale pedal of a vehicle.

. The shift point at which it is desirable to change from hydraulic to direct drive occurs'us'ually when the ratio of turbine speed to pump speed is of the order of 0.7 or less and when the shift is made to direct drive this ratio is changed to a one to one ratio. Thisl change in the ratio requires either that the engine speed by slowed down to the tail shaft speed or the latter accelerated to the engine speed, or a 'combination of both, and this change may .under certain circumstances produce a notic'eable surge in the operation of a vehicle or other drive. In order to eliminate or diminish any noticeable surge occurring when shift is made, the power and speed of the engine may momentarily be decreased at the'instant of shift, as for example by means of an auxiliary throttle or an overrule mechanism acting momentarily on the main throttle or by a momentary ignition cut out. Such an arrangement requires an impulse operative at the time when shift ismade, and the .present arrangem'entfmay if. desired include means for providing such an .impulse as is more or less diagrammatically shown in Fig. 2. As shown in this figure the casing Ill carries a switch mechanism indicated generally at 256 for delivering the -desired impulse through a circuit yinclicated by the wires 258 and 260. In the embodiment-r illustrated, wire 258 terminates in a fixed contact 262 while the wire 260 is connected to a pivoted lever 264 having a projecting arm 266 adapted to be contacted and moved by the end of the lever arm 218. The other arm 268 of lever 266 is resilient and provided with a contact 210 located to make contact with the contact 262 when the lever is turned clockwise as viewed in the figure. The lever is biased to neutral position by springs 212 and 214.

When shift is made from hydraulic to direct drive the end of the lever arm 2 IB moves to the left as seen in Fig. 2 and contacts the lever arm 266 to momentarily turn the lever and close the electrical circuit to provide an impulse for momentarily reducing the engine speed in any desired manner. This impulse is only momentary since the lever 2 IB passes the lever arm 266 which is returned to neutral position by the springs 212 and 214. When shift is made from direct drive to hydraulic drive no decrease of input speed is required, even momentarily. When this shift is made the lever arm 2I8 moves to the right and passes the lever arm 266, momentarily turning the lever counter-clockwise, which movement, however, has no effect on the electrical circuit;

In order to obtain relatively high stall torque Characteristics with the minimum number of rows of blading, and a rapid rise in eiciency of operation of the converter as the turbine or driven shaft accelerates from stall, it may be' desirable to provide what may be termed a double rotation type of converter in which the reaction blading, instead of being rotationally fixed, is mounted so as to be able to rotate in a direction counter to that of the pump, the counter-rotating blading being mechanically connected to the forwardly rotating turbine member by suitable gearing so as to apply additional output torque to the driven shaft of the device. The range of relative speed between the driving and driven members over Which the double rotation type of converter is efficient is comparatively limited as compared with the efficient speed range of a single rotation converter in which the guide or reaction blades are held stationary, and it has heretofore been proposed to provide a converter structure in which both double rotation and single rotation operation may be obtained, the

converter Operating in the low speed range as al double rotation converter and shifting to single rotation operation in the higher speed range.

As in the previously described relation between single rotation converter operation and direct drive, there is also a shift point which occurs at a certain speed relation between the input and output members of a converter of the double rotation type, at which shift should be made from double rotation operation to single rotation-operation or vice versa, and in another of its aspects the present invention contemplates the provisionstr-action previously described :in .connection with the embodiment shown *in Fig. 1 and related figures, like or equivalent parts bearing the :same reference numera-Is.

In the present Vconstruction the sleeve portion '50 of the reaction member .is provided at its rearwar-d endi'with a .gear 216 lconstituting zthe -sun gear -o'f a planetary gear train having planets 218 mounted on Ia planet -carrier .2 80 :and meshing with -a ring gear 2-92 :formed on theturbine member 28. Between an extending sleeve portion of the vcarrier 289 Iand ya similar sleeve .portion of the stationary casing 'part Lilla vthere .is located an :automatic one-way or over-.running brake rcompri'sing engaging elements 2,84 arranged '-to .permit the planet .carrier '289 to :rotate freely .in the same direction as the pump and l-to prevent its 'rotation .in :counter-direction. A looking braKe, indicated generally at V289 :and in the form of a fiuid pressure actuated multiple disc device vsimilar to clutch 1.2, yis provided for looking the reaction .member to *the stationary housing. This brake comprises a series-of .plates 288sspl'ined on the reaction member -sleeve .5D and a second Vseries of plates 299 ysplined on the istationary lhousing part kl-lia. Operating member 292 vlocated 'in a suitable recess in the .'stationary part Ina is adapted to be actuated by pressure fluid supplied under :the :control :of ithe :master valve member :168 .and an f'automatic :shift valve indic'ated generally :at 2-94, the :position of :which is .determined vby the speed of the .turbine .member relative to thatof 'the 'pump member, :through the :medium :of -whattmay i.be termed a quotient regulating mechanism. This mechanism 'includes a gear .296 interposed between .the :pump driving gear [94 on the :rotating casing lNi .and the pump gear 1256, and agear 298 meshingvvith the teeth .of -gear 96 .on the turbine lmember. Gear S298 :is mounted to have both .rotating and sliding movement relative to the :valve :rod 399. Drive from the gear 'to :the 4valve .rod is :eiiec'ted by means of friction plates 1392 :loadedbyimeans of spring :394. lThe ival-ve rod .390 fis provided with threads 1396 'at yone -endwhichxengagefsimilar threads provided in .the 'hub of,gear1296 'and :intermediate its ends the valveirodisiprovided with a -recessed portion 398 .for controlling vflow :of actuating pressure .fiuid to the Tbralce .Operating member :292.

:Referring 'now more particularly "toiFig. =l:1,-it Will Ibe seen that the pressure :pipe -162 filea'ding from pump L| sz lis :provided :with .a Vbranen .fem leading .to fa third section of kthe 'master lvalve member its which controls communication between this branch-'and the conduit :1319 leading to the'shift'valve 294. 'From the'latteryconduit 3l2lleads to .theibrake Operating member 292. A vent .conduit y3|''4 is also providedleading ffrom the valve chamber of valve'294.

lThe Imanner Vin 4Which the above described mechanism Aoperates fto eiectshift from double rotation operation to 'single rotation -operation and vice versa is as-follows. #As will'beievi'dent fromFig. A9, gear 2 96 v rotates'fin a,- direction counter to that of the pump and gear 298 rotat-es-in'a direction* counter to that ofthe Iturbine imember whenever Vthe'latter ismoving. 'If'we now-'consider the conditions at starting, the gear i296, being driven "from Ithe rotating casing 4-6, is in motion .while 'the gearl'Z-Q, meshing Withithestationary turbine member, tis :also fstationary, but is in :frictional/ drive'relationflwith thetvalve :'rod 399adue fto the friction .discsi 3'02. iConsequently, due .to the friction :force i-exertedliby gear f2198-and tending to keep the valve rod rotationally sta.- tionary while gear 296 turns, the rod is forced to the right as viewed in Fig. 9 (downwardly as viewed in Fig. 11) to the limit of its travel in this direction, which is established by collar 390a. In this position of the valve, pressure fluid is cut ofi from :the brake 286 and the pressure-chamber of the brake is vented .due to the fact that conduits SHI .and 3|4 are connected through the Valverecess 398.

v.As ythe turbine member begins to rotate, vgear 298 is -rotated in .the same direction as gear 296. From Fig. 9 .it will be seen that the speed ratio between .the 'pump member and gear 296 is :much lower than the speed ratio between the turbine member .28 and gear .299. .In the embodiment illustrated the former is 4substantially a one .to one ratio -whereas the latter is .of the order of a three to one ratio. Consequently, as the speed .of the turbine member increases, the speed :of gear 2-98 increases much 4more rapidly, and at a speed ratio between the pump :and turbine members .of

the converter which is relatively low, for example usually in lthe neigh'oorhood of from 0.25 to 0.30, the speeds .of gears 296 and 298 will -be equalized. During .this period the converter will operate asa double rotation converter, the reaction blades 44 .rotating counter to lthe .direction of the pump and in effect .constituting counter-rotating turbine blades delivering rpower through the planetary.gearingitothe outputmember of -the'transmission As the speed of .the-turbine member relative 'to the 'pump further -increases, the speed of Sgear 298 wil1 exceed that of gear 299 and due to the vfrictionfdrive HWill tend to Overdrive the valve rod 390 relative to gear 296. I:Chis action causes the-threaded connection vbetween Vthe -valve rod and gear 296 Vto shift the valve rod axially to the right as viewed in Fig. 9 (downwardly in Fig. '11) to its opposite limit position, which is as shown in .the figures and in yWhich the brake Operating member is placed in communication with the pressure conduit 3I9 for engagement of -the brake. Engagement of the brake operates -to lock the reaction member yto the stationary housing and thereafter the converter operates in .the higher speed range as a single rotation converter with statonary reaction or guideblades. Under Ithis condition o'f voperation the sun'gear-of'the planetary gearing is lstationary while the ring -gear rotates with the'turbine member. Thisnecessitates the planet carrier Valsoflrotating in 'the forward direction of .the'turbine member, but-aspreviously noted'this .action ispermitted-by the overrunning brake elementsl284.

'From the above it Will-be apparentthat ifthe turbine member .'slows down relative-to the'pump memberso as .to cross the so called shiftpoint'or shift speed, with the result'that gear'298;rotates more slowly than gear '296, the shift valve-'will again bemoved toa position cutting off thesupply .of .operating fiuid to 'the 'brakeand venting the. pressure topermititsrelease.

,=In .the embodiment .illustrated .the .double rotation andsingle rotation operation of-theconverter vis a1so.combined-.with.a direct drive and with-a reversing mechanism essentially-thel same as that :previously :described :in :connection i with Fig. '1. :Aso/illibe:seenfromzthe. drawings the pressure conduit H2 'leading from :the-master control valve communicates with "the chamber 132 tand, through fports .190 :and l92,f is placedf in communication Lwith the 'I hydraulic chamber =24.

among? The pressure oonduit H communicates through a port I'Ina in the sleeve of the reaction member to the space between this member and the turbine member, from Which space communication is established through channels H16 and 21115 to the chamber 280 and from the latter actuating fluid is delivered to the direct driveclutch 12.

In the present arrangement the channel E86 leading to the radial conduits 2I0 for supplying pressure fluid to the control valves E24 is in communication with pressure conduit Ifi, rather than in communication with the pressure conduit H2 as in the embodiment shown in Fig. 1. This gives the result that when in hydraulic drive only the lower or return pressure of the hydraulic fluid is admitted to the synchronizing clutch, but sufiicient pressure may -be maintained even under this condition to enable this clutch to be operated.

When in direct drive the reaction member obviously must be permitted to rotate in the same direction as the pump and turbine members, and in the embodiment illustrated in Fig. l this is automatically accomplished through the action of the overrunning clutch by means of which the reaction member is held against counter-rotaoperation of the converter must be released When- 2 ever shift to direct drive is made, and this is accomplished automatically by providing the valve housing [56 of the master control valve E64 with a vent port 316 located to be blocked from communication With the pressure channel 3143 leading to the valve 294 whenever the master valve is in the position corresponding to hydraulic drive but arranged so as to be placed in communication with the conduit 310 whenever the master valve is moved to the position providing direct drive. Thus, regardless of the position of valve 294, the fluid actuated brake for holding the reaction member stationary is relieved of pressure whenever direct drive is established so that the brake is disengaged and the reaction member is enabled to rotate freely in the same direction as the pump and turbine members. Under direct drive conditions the pump and turbine members rotate forwardly at the same speed which requires that the planet carrier of the planet gear .I

connecting these members also rotate forwardly at the same speed. This is permitted by the action of the overrunning clutch 284 which overruns under direct drive conditions in a manner similar to that which occurs when the apparatus is set for single rotation converter drive.

Because of the difference in the clutch construction required in order to employ double rotation operation, the automatic shifting arrangement for effecting direct drive under the influence of the movable ring 62 and the Operating rod 68 (Fig. 2) associated With the overrunning clutch is omitted, the shift from converter operation to direct drive and vice versa being effected through the medium of operation of the mechanism actuated by movement of the lever 234, which may readily be actuated automatically in response to predetermined conditions indicative of little or no torque increase through the hydraulic drive so that a shift to direct drive is indicated.

While for the purpose of illustrating the principles of the invention in its various aspects, particular forms of converter mechanism have been chosen by way of example, it will be apparent that many changes in the form and construction of the apparatus may be made without departng from the spirit and scope of the invention and that certain of the features of the invention may be employed to the exclusion of others. It is therefore to be understood that the invention includes all forms of apparatus falling Within the scope of the appended claims.

The generic subject matter and subject matter specific to the single rotation form of converter illustrated in Figs. 1 to 8 inclusive is claimed in my co-pending continuation-in-part application Serial No. 100,041, filed June 18, 1949, the claimed subject matter in this application being restricted to the double rotation form of apparatus which is not embodicd in the disclosure in the aforesaid continuation-in-part application.

What is claimed:

1. A power transmission comprising a hydraulic Variable speed torque converter having rotatably mounted driving and driven members and a rotatably mounted reaction member, rotationally stationary means, gearing interconnecting said reaction and driven members for rotation of the reaction member in a direction counter to that of the driven member by hydraulically applied reaction torque, means comprising a brake associated with said gearing engageable to cause reaction torque to be transmitted to said stationary means when the reaction member rotates in said counterdirection and dsengageable to permit the reaction member to come to rest and to rotate in the same direction as the driven member while the driven member is rotating, means providing an alternative driving connection between said driving and driven members including a fluid pressure actuated driving clutch, a fluid pressure actuated looking brake for connecting said reaction member and said stationary means, and means for supplying Operating fluid to said driving clutch and to said locking brake comprising control valve means constructed to selectively engage and disengage said brake in accordance with predetermined Operating conditions when said driving clutch is disengaged and to insure release of said brake whenever said driving clutch is engaged.

2. A transmission as set forth in claim 1 in which said control valve means includes a shift valve movable from a first position for effecting disengagement of the looking brake to a second position for effecting engagement of the brake and a master valve movable from a first position for effecting disengagement of the driving clutch to a second position for efiecting engagement of the driving clutch, said master valve including means for cutting off the supply of operating fluid to said shift valve whenever the master valve is moved to its said second position.

3. A transmission as set forth in claim 2 including an automaticaly operable quotient regulator responsive to Variations in the ratio of the speed of the driven member to that of the driving member for positioning said shift valve in its said first position When said ratio is below a predetermined value and positioning said shift valve in its said second position when said ratio exceeds said value.

4. In a power transmission, a hydrodynamic torque converter having driving, reaction and driven members selectively operable in a single hydraulic circuit to transmit power in different torque converting driving relations from the driving to the driven member, a fluid pressure actuated control system including a control valve mov able to different positions for controlling the flow of pressure fluid to provide in alternation said different torque converting driving relations between said members, a first element rotatable at a speed indicative of the speed of the driving member, a second element rotatableat a speed indicative of the speed of the driven member, and means operatively connecting both of said elements With said control valve for causing the control valve to move from one to the other of said positions when the speeds of said elements cross.

5. Apparatus as defined in claim 4 in which said control valve is turnably mounted and is frictionally connected With one of said rotatable elements to be turned thereby.

6. Apparatus as defined in claim 4 in which said control valve is rotatably mount'ed and axially shiftable between said positions, and in which driving connections are provided between said elements and said valve and said driving connections including a friction connection Vbetween one of said elements and said valve 'for turning the latter and a connection between lthe other of said elements and said valve for axially shiftng the valve when the speeds of said elements cross. I

7. A hydrodynamic torque converter Vconstructed for alternative operation as a single rotation cr double rotation converter for transmitting power from a driving member'to adriven member including rotatably mounted reaction and turbine wheels, means for tr'ansmittng torque in the same direction to said driven member from said wheels while the Wheels are rotating in opposite directions, 'releas'able brakin'g means for holding said reaction ywheel rotationally stationary, fiuid pressure actuatedme'ans for causing engagement of said bra'king "means including a control valveland means responsive to predetermine variations'in'the speed kratio between said driving and driven *membersI for mov- 20 ing said valve 'to effect engageme'nt 'or release of said braking means.

8. Apparatus as defined in clairh 7 in which said controllvalve is turnably lmounted and' axially shiftable between two vterminal positions to cause disengagement of said brake in a first position and to cause engagement of said brake in a second lposition and said means being operative to maintain the valve in said first position whenever the speed of the driven member relative to that of the driving member is below a predetermined ratio 'and to 'maintain the 'valve in said second position whenever said ratio exceeds said predetermined value.

References Cited in the file of this patent UNITED sTATEs PATEN'rs Number Name Date Re. 22,967 Nutt Jan. 27, 1948 1,960,705 Kochling May 29, 1934 1,970,236 Kluge'et al Aug. 14, 1934 2,005,44'4 Weiss June 18, :1935 2,018,6l6 Martyrer Oct. 22, 1935 2,037,252 Martyrer Apr. 14, 1936 2,089,590 Walti Aug. 10, 1937 2,l34,398 'Cotterman Oct. 25, 1938 l2,222',618 Jandasek Nov. 26, 1940 2,302,714 Pollard Nov. 24, 1945 2,373,453 Brunken Apr. v10, 1945 2,3'7430'3 Osborne Apr. 24, 1945 2,408,95l Pollard Oct. 8, 1946 2,442,840 Carnagua June 8, 1948 2,449,586 Carnagua Sept. 21, 1948 2,449,608 Le'May Sept. 21, 1948 2,456,132 Lapsley -1-1 Dec. 14,1948 2,456,328 Schneider Dec. 14, 1948 2,568,007 Jandasek r Sept. 18, 1951 FOREIGN tPATENTS Number Country Date i 452,415 Great Britain Aug. 21, 1936 

